Multiple cylinder pump



Aug. 15, 1944.

P. c. TEMPLE IULTIPLE CYLINDER PUIP Filed 001;. 9. 1942 7 Sheets-Shani: 1

PAUL C. TEMPLE w I A III Aug. 15, 1944. P. c. TEMPLE v -IUL'.I.'IPLE CYLINDER PUIP 7 Sheets-Sheet 2 Filed Oct." 9. 1942 Plum. 6. TEMPLE Aug. 15, 1944.

P. C. TEMPLE I IULTIPLE CYLINDER PUII Filed 001;. 9, 1942 7 Sheets-Sheet 3 PAUI. C. TEMPLE P. C. TEMPLE IUL'IIPLE CYLINDER PUIP Jinn/wk" l PAUL 6. TEMPLE HE \V Aug. 15, 1944.

. P. c. TEMPLE 2,356,101

MULTIPLE CYLINDER PUMP Filed bot. 9, 1942 7 Sheets-Sheet 5 Aug. 15, 1944.

3 wuwvbom FA UL C. TE PLE P. c. TEMPLE 2,356,101

MULTIPLE CYLINDER PUMP 7 Sheets-Sheet 7 Filed Oct. 9, 1942 gwvc/wbo v PAUL (J. TEMPLE Patented Aug. 1944 UNITED! srA'rr-zs PATENT- oral-cs MULTIPLE CYLINDER. rum

Paul 0. Temple, Decatur. m., assignor to A. w. Cash Company, Decatur, 111., a corporation of Delaware Application October 9, 1942, Serial No. 461,399

8 Claims.

This invention relates to hydraulic transmissions, and more particularly to a multiple cyl-.

inder pump or sender capable of furnishing pressure fluid at a desired rate for the operation of a motor or receiver.

Mechanisms of this general type are ordinarily driven at a constant speed in one direction, provision being made to vary the pump displacement and to reverse the direction of the fluid flow, so that the speed and direction of rotation of the motor can be controlled. It-is also customary to supply make-up fluidto the inlet of the pump justment of the displacement has required a considerable manual effort on the part of operator.

It is one object of the invention to provide a multiple cylinder pump of the variable displacethe - ment type which will be highly eflicient in operation, and comparatively free from friction and wear. I

It is a. further object of the invention to provide a multiple cylinder pump of the variable displacement type which will be comparatively simple and inexpensive to manufacture and thoroughly dependable in service.

It is a further object of the invention to provide a multiple cylinder pump of the reversible flow type having a simple and dependable means of supplying make-up fluid automatically to the inlet of the pump regardless of the direction of flow.

It is a further object of the invention to provide a. multiple cylinder pump of the reversible flow type having simple and dependable means for relieving excess fluid pressure from the outlet side of the pump regardless of the direction of flow.

It is a further object of the invention to provide a multiple cylinder pump having a simple appended hereto.

tion resides in the combination of parts set forth in the specification and covered by the claims Referringto the drawings erence numerals indicate like parts, I

Fig. 1 is a sectional plan view of the pump or sender of a. hydraulic transmission, the section line 2-2 of Fig. 1:

and dependable meansfor adjusting the pump displacement quickly and accurately, the said on the part of the operator.

With these and other objects in view, as will being taken on the line l-l of Fig. 2; t

Fig. 2 is a view of the pump partially in front elevation and partially in section taken on the Fig. 3 is a section taken substantially on the line 3-3 of Fig. 2;

Fig. 4 is a section taken on the line 4-4 of Fig. 1; a

Fig. 5 is a section taken on the line 55 of Fig. 1;

Fig. 6 is a section taken on the line 6-6 of Fig. 2;

Fig. 7 is a section taken on the line 1-1 of Fig. 1; I

Fig. 8 is a fragmentary view of the pump partially in rear elevation and partially in section taken on the line 8-8 of Fig. 6;

Fig. 9 is a fragmentary view taken on the line 99 of Fig. 8;

Fig. 10 is a section taken on the line l0-l0 of Fig. 3;

Fig. 11 is a front elevation of the pump and its associated supporting base, the base being partially broken away for cleamess of illustration; and

Fig. 12 is a, planview of the apparatus.

The embodiment illustrated comprises a' casing l5 which is mounted upon a hollow base l6 (Fig. 11), this base forming a reservoir for oil. Within the casing,- and as best shown in Fig. 1, there is provided a. main rotor H, which is supported by a pair of axially spaced ball bearings I9 and 20. This rotor is provided with a shaft 2| which extends outwardly from the casing for connection with a suitable source of power. An auxiliaryrotor 22 is mounted within the casing in spaced relation with the main rotor, this auxiliary rotor being supported by a pair of axially spaced ball bearings 23 and 24 carried by a member 25. As shown in Fig. 2, this member 25 is in the form of a yoke which is pivotally sup,- ported by a pair of aligned pins or trunnions 26 mounted on the casing walls. The axes of the two rotors are in a common horizontal plane, and the trunnions 26 are positioned in a vertical line which passes through both of these axes. be apparent to those skilled in the art, the inven- 5B In the drawings the yoke 25 is shown in its cenillustrating one embodiment of the invention, and in which like reftral' or neutral position, with the axes of the rotors aligned. By swinging the yoke in either direction about its trunnions, the axis of the auxiliary rotor will be made to intersect the axis of the main rotor; at an obtuse angle.

versal joints. In the preferred construction illustrated each of these joints comprises a ring 29 which is pivotally connected to the corresponding rotor by means of two aligned pins 30 and to the adjacent end of the spindle byimeans of two similar aligned pins 3| spaced ninety degrees from the pins 30. The two pins 3| at one end of the spindle are located in a common plane with the two pins 3| at the opposite end of the spindle, so that the two universal joints are in the same phase. Furthermore the line of centers of the trunnions 26 is equidistant from both universal joints, so that the axis of the spindle will always intersect the axes of the two rotors at equal angles. With this construction the angular velocities of the two rotors will always be equal. In order to facilitate assembly and permit the chang of length required by adjustment of the yoke, the spindle 28 is formed. of two telescoping parts connected by multiple splines;

A series of fifteen expansible and contractiblefluid displacement units-isarranged in a circle around the coupling spindle 28. Each of these units preferably includes two telescoping parts in the form of a cylinder 33 and a piston 34 slidable therein. The opposite ends of each displacement unit are connected to the adjacent rotors l1 and 22 by swivel joints, preferably of the ball-andsocket type. As illustrated the rotor I1 is provided with a circular series of spherical members 35 which fit within similarly shaped sockets 36 in the adjacent ends of the cylinders 33, and the rotor 22 is provided. with a circular series of spherical members 31'which fit within similarly shaped sockets 38 in the adjacent ends of the pistons 34. With this construction, and the yoke adjusted to either side of its neutral position, the pistons will make one complete stroke in each direction for every revolution of the rotors. The axis of each cylinder-piston unit will always be in a direct line connecting the centers of the corresponding spheres 35 and 31, and there will accordingly be no side thrust or cramping forces involved between the pistons and their respective cylinders. It is therefore. feasible to provide much greater angular adjustment for the yoke than would otherwise be the case, thus increasing the piston stroke and the capacity of the pump for a' given size and weight. To facilitate assembly, the sockets 36 are in part formed in collars 39 attached by screw threads to the ends of thecylinders, and the sockets 38 are in part formed in collars "attached by screw threads to the ends of the pistons. The spherical members 35 are-provided with screw threaded shanks 42 secured in the rotor I1, and the spherical mbers 31 are provided with tapered shanks 43 which are secured to the rotor 22 by means of nuts 44.

Provision is made for the admission and discharge of fluid to and from the cylinders 33 in proper synchronism with the movements of the various parts. For this purpose each of the spherical members 35 is provided with a central bore 46 which extends through the shank 42 and.

communicates with a duct or passage 41 formed in the rotor I1. Each of the passages 41 leads to a port 43 which opens radially outward in a cylindrical portion of the rotor between the ball bearings l3 and 20. This portion of the rotor flts rather closely within a cylindrical bore 43 in the casing I5. The bore 48 is provided with two diametrically opposed circumferentially extending grooves .or chambers 5| and52 located in line with the ports 48 and arranged to be connected with external pipes 53 and 54 respectively. These pipes may lead to a suitable hydraulic motor (not shown). The chambers are separated by two diametrically opposed abutments 55 and 56 (Fig. 3) which lie in the horizontal axial plane. The

width of these abutments,-measured circumfer entially, slightly exceeds the circumferential width of the ports 48, so that the ports'will com-. municate with the chambers 5i and 52 alternately, but no port will communicate with both chambers simultaneously. For convenience in manufacture, the rotor i1 is formed of two flanged pieces which are fastened together by four pins 51 (Fig. 3). The passages 41 can be readily obtained by drilling, the unwanted openings being pluggedas shown in Fig. 1.

The cylinders and pistons are so constructed as to substantially eliminate all friction and wear from the ball-and-socket Joints. This is accom- "plished by exposing each of the Joints to the fluid pressure within the corresponding cylinder,

over a projected area substantially equal to and preferably very slightly less than the effective area of the piston. For this purpose each piston 34 is provided with a passage 59 (Fig. 1) which extends centrally therethrough so that fluid from the cylinder will be admitted into direct contact with the spherical member 31. At the end adja cent the member 31 this passage 59 is formed with a counterbore or enlargement 60 having a diameter slightly less than the diameter of the piston. In addition, the bore of each cylinder 33 is slightly contracted at 6|, adjacent the spherical member 35, to a diameter slightly less .than that of the piston. With this construction there will be only a very slight axial thrust on each cylinder and piston, caused by the fluid pressure on the very small area represented by the difference in area between a circle having a diameter equal to that of the piston and a circle having a diameter equal to that of the enlargement 6!! or the contracted portion 8 I This slight thrust is desirable since it minimizes leakage of fluid past the'ball-and-socket Joints without imposing any appreciable friction load thereon. In practical eifect this construction applies the fluid pressure directly to portions of the rotors, i. e., the spherical members, rather than indirectly through the medium of the cylinders and pistons. These latter parts are used simply to confine the fluid and not to transmit heavy mechanical forces to or from the fluid as in prior mechanisms.

Means is preferably provided to supply makeup fluid to the inlet of the pump at an appreciable pressure in order to ensure complete filling of the cylinders at each stroke. For this purpose I have shown a geared rotary pump 63 comprising a driving gear 64 (Fig. 8) keyed to the shaft 2| and a. driven gear 65 rotatably mounted on a stud G6 and meshing with the gear 64. These two gears cooperate-in known manner to transfer fluid from an inlet chamber 68 (Fig. 6) to an outlet chamber 69. Between these two chambers there is provided a port 10 controlled by a relief valve ll loaded by a helical compression spring I2, With this construction a substantially constant fluid pressure will be maintained in the chamber 88, any excess fluid being returned to the chamber 88 through the port I8. Fluid is delivered to the inlet chamber 89 from the reservoir I8 through a pipe 18 having an inlet screen termined by theadjustment of the yoke 28. For

this purpose the mechanism I8 is shaped to provide an upper chamber I8 which is connected with the chamber 9| by a passage I9, a lower chamber 88 which is connected with the chamber 92 by apassage 8|, and an intermediate chamber 20 82 which receives fluid directly from the pipe 18.

A check valve 84 is provided between the intermediate chamber 82:and the upper chamber 18, and a second check valve 88 is provided between the intermediate chamber and the lower chamher 88. Both of these check valves are arranged to open in the direction of flow out of the intermediate chamber, and they are preferably urged toward their closed positions by light helical compression springs 89. Preferably the two check valves are axially aligned and provided with stems 81 which extend toward one another in abutting relation and of such lengths that when one valve is closed the other valve will be held open. Two pressure relief valves 89 and 98 are 3 provided between the upper and lower chambers I8 and 88, these valves being urged toward their seats-by heavy helical compression springs 9|. The valve 89 opens in the direction of-flow out of the upper chamber I8, and the valve. 99'opens' in the direction of flow out oi! the lower chamber 88. Ii the pressure in either of the chambers Si or 8: tends to become excessive, one. or-stlie other of the valves 89 and 98 will open autoiri'atically to allow fluid to flow directly from the high 49 pressure side of the main pump to the low pressure side thereof. It will be apparent that one of the check valves 94 and 88 will be held closed bythe pressure at the discharge side of the main pump, the other check valve being open to allow 50 alignment with the upper trunnion. 28. The other flow of make-up fluid from the geared pump 83 to the inlet side of the main pump.

The yoke 25 can be moved about its trunnions 28, to control the volume and direction of the fluid flow through the main pump, by a hydrauliso cally actuated mechanism, which in the embodiq ment illustrated is controlled manually. For'th s purpose, as shown in Fig. 4, two horizontal cylinders 99 are mounted one above the other onone side of the casing I5, and two horizontal cylinso ders"94 are mounted one above the other on the other side of the casing. The inner ends of these cylinders open into the casing. A single-act ng piston is slidably mounted within each of the cylinders 93, and a single-acting piston 98 is 85 mounted within each of the cylinders 94. Each oi the four pistons is joined by a connectingrod 9I'to the yoke 25. By admitting fluid to the cylinders 98, the yoke can be swung in one direction,

and by admitting fluid to the cylinders 94 the 78 yoke can be swung in the opposite direction.

The admission and discharge of fluid from the cylinders 93 and 94 are controlled by a four-way pilot va-lve mechanism including a casing 99 (Figs.

3 and 10) shaped to provide two spaced chambers 78 I98 and I 8| which I shall refer to as a forward" chamber and a "reverse chamber respectively. Between these two chambers there is provided an' inlet chamber I82 which is supplied with pressure fluid through a pipe I84 connected with the pipe I9. The forward chamber I88 is connected with the two cylinders 93 by a pipe I89,

tions 8 and I II which normally close the ports leading to the chambers I88 and IN respectively. The pilot valve is so constructed that when it is moved in either direction from the neutral position illustrated, it will admit pressure fluid from the pipe I84 to one of the chambers I88 or IM while allowing fluid to exhaust from the other chamber into the main pump casing I5; whence, the fluid will return through a drain pipe II2 (Fig. 11) to the reservoir I8.

The pilot valve mechanism illustrated is arranged for manual control, and for this purpose there is provided a hand lever II4 (Fig. 10) which is secured to the upper end of a vertical shaft -I I8 rotatably supported in the casing 99. This hand lever is provided with a pointer I it which travels over a scale I II to indicate the posit on of adjustment. A lever arm I I9 is secured to the lower end of the shaft II, this arm being connected by a link I28 to one end of a floating lever I 2I. The other end of the lever III is connected to the pilot valve I89. The lever I2I is i'ulcrumed intermediate its length on one end of a link I23 whicn isconnected at itsother end to a lever I24 (Fig.

2), the lever I24 being fulcrumed intermediate its length on a pin I29 secured to the casing 99.

' The lever I24 is moved about its fulcrum in response to movements of the yoke 25 about its trunnions 28 by a suitable compensating mechanlsm,so that the pilot valve will be restored to neutral when the yoke has reached a pos tion corresponding to the position of the hand lever II4. As shown in Fig. 2, a lever I2! is secured at one end to a fulcrum pin I29 which is rotatably mounted in the casing 99 directly above and in end of the lever I2'I is connected to the yoke 25 by means of a stud I29. A pin I3I projects upwardly. from the lever I21 intermediate its length, and this pin is straddled by a fork I32 on the adjacent end 01 the lever I24. Preferably a pointer I34 is secured to the upper endof the fulcrum pin I28 to travel over a scale I89 (Fig. 10) and thereby indicate the position of the yoke 25.

Theoperation of the invention will now be apparent from the above disclosure. The shaft 1 2| will be rotated in the direction of the arrow in-Fig. 3 by any suitable source of power. The geared pump 99 will draw oil from the reservoir I 6 throughthe pipe I9 and supply this oil at a substantially uniform pressure of say 100 lbs. per

' square inch to the pipes 15 and I84, the excess oil hand lever H4 in a counter-clockwise direction as viewed in Fig. 10, which will swing the floating lever I2I about its fulcrum on the link I23 and slide the pilot valve I09 to the left, allowing oil under pressure to flow from the pipe I04 through the chambers I02 and I to the pipe I05 and the cylinders 93. The pistons 95 in Fig. 4 will move to the right, causing the yoke 25 and the pistons 96 to also move to the right. Oil will exhaust from the cylinders 94, through the pipe I06 and chamber IN to the interior of the casing I5. This movement of the yoke 25 about its trunnions 26 will swing the lever I21 (Fig. 2), which in turn will actuate the lever I24 and link I23 in the proper direction to return the pilot valve I09 to its neutral position. When this occurs, the yoke will come to rest, having moved the pointer I34 over the scale I35 to a position corresponding with that indicated on t.'.e scale II! by the pointer II6. Because of the angular relationship which now exists between the axes of the two rotors I1 and 22, the pistons 34 and the cylinders 33 will have relative reciprocating movements. This will cause oil to be drawn into the cylinders 33 through the pipe 53 and chamber 5|, and delivered from the cylinders through the chamber 52 and pipe 54 to the hydraulic motor to operate the same in a forward direction. The pressure of this delivered oil will hold the check valve 85 (Fig. 5) closed and the check valve 04 open. Consequently, oil from the geared pump 63 will flow past the check valve 84 and through the chamber I8 and passage I9 to the chamber 5| in suflicient quantities to make up for any internal leakage from the main pump and also ensure complete filling of the main pump cylinders at each stroke. If the pressure in'the delivery chamber 52 of the main pump should become excessive, the relief valve 90 will open automatically to allow oil to escape into the chamber 5|. To reverse the hydraulic motor, the operator need merely turn the hand lever H4 in a clock- 'wise direction to the other side of its neutral position. This will move the pilot valve I09 to the right in Fig. 10, admitting oil to the cylinders 94, and moving the yoke 25 to the other sideagainst excessive oil pressure in the chamber 5|.

It will be understood that regardless of the direction of oil flow, the volume of the oil flow and the resultant speed of the hydraulic motor will be dependent upon the size of the angle between the axes of the two rotors I1 and 22, as determined by the angle through which the hand lever I I4 is moved from its neutral position. The pointer I34 will indicate to the operator the position of the yoke 25, and if the various parts are functioning properly this position will always correspond to that of the pointer. I I6.

From the above disclosure, it will be apparent that the invention provides a highly eflicient multiple cylinder pump which will be comparatively free from friction and wear, relatively simple and inexpensive to manufacture, and thoroughly dependable in service. The direction of fluid flow can'be readily reversed, and make-up fluid will 76 be supplied to the pump inlet automatically regardless of such reversal. The pump is also protected against excessive discharge pressures for either direction of flow. The pump can be reversed and its capacity readily varied by the simple adjustment of a single hand -lever.

This is a continuation in part of my application No. 456,523 filed August 28, 1942, and abandoned July 31, 1943.

Having thus, described my invention, what I claim as new and desire to secure by Letters Patent is:

1. A fluid pump comprising a casing, a main rotor rotatably supported in the casing, a yoke pivotally mounted in the. casing, an auxiliary rotor rotatably supported in the yoke, means connecting the rotors for simultaneous rotation in the same direction, an annular series of fluid displacement units located between the rotors and each including a cylinder and a piston, means providing ball-and-socket joints between the opposite ends of each unit and the respective rotors, means to admit fluid to the cylinders as the units lengthen and to withdraw fluid from the cylinders as the units contract, a hydraulic motor connected to the yoke to move the same about its pivot, a pilot valve arranged to control the flow of fluid tothe motor and having a neutral position, a control device for the pilot valve, and compensating mechanism connecting the yoke with the pilot valve to return the same to its neutral position as the yoke reaches a position corresponding to the position of the control device. I

2. A fluid-pump comprising a casing, a main rotor rotatably supported in the casing, a yoke pivotally mounted in the casing, an auxiliary rotor rotatably supported in the yoke, means connecting the rotors for simultaneous rotation in the same direction, an annular series of fluid displacement units located between the rotors and each including a cylinder and a piston, means providing ball-and-socket joints between the opposite ends of each unit and the respective rotors, means to admit fluid to the cylinders as the units lengthen and to withdraw fluid from the cylinders as the units contract, a hydraulic motor connected to the yoke to move the sameabout its pivot, a pilot valve arranged to control the flow of fluid to the motor and having a neutral position, a lever connected to the pilot valve, a movable fulcrum for the lever, a control device for the pilot valve connected to the lever, and compensating mechanism connecting the yoke with th lever fulcrum to move the same and return the pilot valve to its neutral position as the yoke reaches a position corresponding to the position of the control device.

3. A- fluid pump comprising a casing, a main rotor rotatablysupported in the casing, a yoke pivotally mounted in the casing, an auxiliary rotor rotatably supported in the yoke, means connecting the rotors for simultaneous rotation in the same direction, an annular series of fluid displacement units located between the rotors and each including a cylinder and a piston, means providing ball-and-socket joints between the opposite ends of each unit and the respective rotors, means to admit fluid to the cylinders as the units lengthen and to withdraw fluid from the cylinders as the units contract, a hydraulic motor connected to the yoke to movethe same about its pivot, means indicating the position of the yoke, a pilot valve arranged to control the flow of fluid to the motor and having a neutral position, a control device for the pilot valve, means indicating the position of the control device, and

compensating mechanism connecting the yoke.

with the pilot valve to return the same to its neutral position as the yoke reaches a position corresponding to theposition of the control device.

4. A fluid pump comprising a casing, a main rotor rotatably supported in the casing, a yoke pivotally mounted in the casing, an auxiliary rotor rotatably supported in the yoke, means connecting the rotors for simultaneous rotation in the same direction, an annular series of fluid dis-' of the said two cylinders, connecting rods joining the single-acting pistons with the yoke, a pilot valve arranged to control the flow of fluid to and from the said two cylinders and having a neutral position, a control device for the pilot valve, and compensating mechanism connecting the yoke with the pilot valve to return the same to its neutral position as the yoke reaches a position corresponding to the position of the control device.

5. A fluid pump comprising a casing, a main rotor rotatably supported in the casing, a yoke pivotally mounted in the casing, an auxiliary rotor rotatably supported in the yoke, means connecting the rotors for simultaneous rotation in the same direction, an annular series of fluid dissaid units to actuate the same, two chambers each of which is adapted to serve as an inlet chamber while the other serves as an outlet chamber, means to connect each of the said units with the said chambers alternately, means to reverse the fluid flow through the pump during the continuous rotation of the shaft in one direction, means providing an intermediate chamber, a make-up pump driven from the shaft and arranged to deliver pressure fluid to the said intermediate chamber, separate passages connecting the intermediate chamber with each of the said two chambers, and a check valve in each passage arranged to open in the direction of flow out of the intermediate chamber. I

'7. A fluid pump comprising a casing, a series of fluid displacement units located within the casing and each including a cylinder and a pis- 7 ton, a drive shaft rotatably mounted in the casplacement units located between the rotors and each including a cylinder and a piston, means providing ball-and-socket joints between the opposite ends of each unit and the respective rotors, means to admit fluid to the cylinders as the units lengthen and to withdraw fluid from the cylinders as the units contract, two pairs of cylinders mounted on the casing on opposite sides thereof with their inner ends open into the casing, a single-acting piston slidably mounted within each of the last-mentioned cylinders, connecting rods joining the single-acting pistons with the yoke, a

pilot valve arranged to control the flow of fluid ing, means connecting the drive shaft with the ing, means connecting the drive shaft with the said units to actuate the same, two chambers each of which is adapted to serve as an inlet chamber while the other serves as an outlet chamber, means to connect each of the said units with the said chambers alternately, means to reverse the fluid flow through the pump during the continuous rotation of the shaft in one direction,

ranged to deliver pressure fluid to the said intermediate chamber, separate passages connecting the intermediate chamber with each of the said two chambers, a check valve in each passage arranged to open in the direction of flow out of the intermediate chamber, and means effective, when either of the check valves is closed, to open the other check valve. I

8, A fluid pump comprising a casing, a series of fluid displacement units located within the casing and each including a cylinder and a piston, a drive shaft rotatably mounted in the casing, means connecting the drive shaft with the said units to actuate the same, two chambers each of which is adapted to serve as an inlet chamber while the other serves as an outlet ranged to open in the direction of flow out of the intermediate chamber, and two spring-loaded relief valves to control flow of fluid between the said two chambers and opening in opposite directions of flow. Y I

- PAUL C. TEMPLE. 

